Multiple side punching machine



NOV. 10, 1970 s, s, zmmgmvhl 3,538,735

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ATTORNEY United States Patent O 3,538,735 MULTIPLE SIDE PUNCHING MACHINESanford S. Zimmerman, Westport, Conn., assignor to Nathan Dolberg,Fairfield, Conn. Filed Apr. 27, 1967, Ser. No. 634,217 Int. Cl. B21d43/28; B26d 7 06 U.S. Cl. 72-324 8 Claims ABSTRACT OF THE DISCLOSURE Anapparatus for simultaneously punching or forming apertures or shapeddepressions in the side wall of tubular parts, the apertures ordepressions being formed in a variety of patterns of circumferentialand/or axial rows. A plurality of tool carrying, radially movable ramsare driven inwardly and outwardly in response to unidirectional movementof actuating cams carried by an oscillating cam carrier, and automaticpower means actuate both the carrier and an ejecting mechanism when anoperating cycle is completed.

CROSS-REFERENCE This application discloses and claims improvements inthe invention claimed in copending application Ser. No. 498,508, filedOct. 20, 1965, now Pat. 3,316,787 in the name of Thomas E. Lambro andassigned to the assignee of this application.

BRIEF SUMMARY The present invention relates to improvements in a machinefor simultaneously punching or forming a plurality of apertures orshaped depressions in the side wall of relatively short tubular -blanksor semifinished articles of similar shape.

The machine consists generally of a frame having a substantiallyhorizontal surface to which is secured a central die post around whichthe part to be worked is placed. A plurality of punching units aredisposed in peripherally spaced relationship around the die post, eachunit having a radially reciprocable ram and ram guide assembly, and aworking tool and tool guide assembly. An annular carrier is rotatablymounted on the frame in concentric relationship with the punching units,and carries a plurality of actuating cams which are interconnected withthe rams of the punching units for driving the latter radially inwardlyand outwardly in response to oscillatory movement of the carrier and thecams. A pneumatic power unit is mounted on the frame and connected tothe carrier for oscillating the latter. An ejecting mechanism is mountedon the frame beneath the die post and has means for ejecting a part fromthe die post when the working operation on the part is completed.

One of the significant aspects of the present invention resides in thecam construction and placement on the annular carrier. Specifically thisis that the cams have radially spaced rectilinear camming surfaces forforcibly driving the rams both inwardly and outwardly, with both cammingsurfaces being of the same length and of suflicient length that the ramsare moved through a complete cycle of inward and outward movement inresponse to a single unidirectional movement of the annular carrier andcams between spaced apart limit positions. Thus the power unit, thecarrier and the cams need move only in one direction to effect both apunch and withdraw stroke of the working tools.

Also, the cams are located on the carrier in such manner that therectilinear camming surfaces are perpendicular to the longitudinal axisof the rams and working ICC tools when the latter are in their radiallyinnermost position. Thus, the working force transmitted from the cams tothe rams approaches a maximum as the working tool approaches andpenetrates into the wall of the work part.

Another signicant feature is the provision of means for applying onlydirectly axial forces to the working tools regardless of the extent towhich nonaxial forces are applied to the rams by the actuating cams,thus achieving an extremelyhigh degree of accuracy in locating punchpatterns, such accuracy being in the area of plus or minus .0005 of aninch.

Also, provision is made for adjustment of the working tools in the axialdirection to compensate for wear so as to maintain the same degree ofaccuracy in working operations where the side wall of a part is notpunched through, such as detenting or lancing.

Still further, provision is made for removably connecting both theworking tools and a tool holder to the rams and frame of the machinerespectively in a manner facilitating removal of the tools and toolholder as a unit without having to disassemble any portion of themachine.

Another significant aspect of this invention is the provision of meansfor mounting both the rarn guide assembly on the frame and the cams onthe carrier for angular adjustment to an infinite number of positionswithout any structural modification to the machine, thereby facilitatinga wide variety of both symmetrical and nonsymmetrical punching patterns,and giving the machine greater versatility than was heretofore possible.

Having briefly `described the nature and several important aspects ofthe present invention, it is a principal object thereof to provide amultiple side punching machine having improved working capabilities andproduction efficiency over other machines heretofore known.

Another object of the present invention is to provide a. multiple sidepunching machine which reduces to a minimum the number of movements ofWorking parts which are required to eifect a working cycle of operation.

Still another object of the present invention is to provide a multipleside punching machine in which tool movement is rapid while approachingor moving clear of the Work, but is retarded and is of maximum workingforce when the greatest resistance to penetration of the work part isobtained during the punching operation.

Another object is to provide a machine of the character described whichwill consistently perform to extremely close tolerances, and which hasprovision for rapid adjustment of the parts to compensate for wear andtear on the working tools.

Yet another object is to provide a multiple side punching machine whichis flexible in permitting the selection of a wide variety of punching orworking patterns.

These and other objects and features of the present invention will beapparent from an understanding of the following detailed description ofa preferred embodiment of the invention when considered in conjunctionwith the accompanying drawings in which:

FIG. 1 is a plan view of a multiple side punching machine constructed inaccordance with the principles of this invention, this View showing theparts in f-ull working position;

FIGS. 2 and 3 are fragmentary side elevations of the machine illustratedin FIG. 1;

FIG. 4 is a sectional view taken on the line 4-4 of FIG. l;

FIGS. 5 and 6 are fragmentary plan views illustrating the machine partsin the two opposed Withdrawn or nonworking positions; and

FIG. 7 is a schematic diagram of the pneumatic and electric controls ofthe machine. i

3 DETAILED DESCRIPTION Referring now to the drawings, and particularlyto FIGS 1 and 4 thereof, the general arrangement of the machine is seento comprise a frame in the form of a substantially fiat horizontalsurface which is supported by a plurality of legs I(not shown). Apunching component 12 is mounted on the frame 10 in position tovertically receive and eject parts to be punched, the punching componentcomprising the basic actuating parts 14 of the machine and a workingassembly 16, hereinafter called the tooling which, in the manufacture ofthe machine, must Ibe custom made for each different type of part beingpunched or for each different punch pattern employed. It will thus beappreciated that the machine of this invention is intended for use invery high production lots of identical parts.

A power unit 18 is also mounted on the frame 10* adjacent the punchingcomponent 12 for actuating the latter, and an ejecting mechanism 20(FIG. 4) is mounted on the underside of the frame 10 for ejecting partsafter they have been punched. As actually constructed, the machine alsoincludes various control components which are also conveniently mountedunder the frame 10, these components not being shown in detail since thespecific construction thereof forms no part of the present invention,but are operatively schematically illustrated in FIG. 7 and describedhereinbelow.

The punching component 12 is constructed and arranged to have theactuating parts 14 thereof disposed radially with respect to the tooling16. More specically, a plurality of punching units 2.0, 22, 24 and 26are disposed around the tooling 16 in peripherally spaced relationship,and radially outwardly therefrom there is a corresponding number ofactuating cam assemblies 28, 30, 3'2 and 34. The cam assemblies aremounted on an annular carrier or ring 36 which is oscillated over apredetermined angle between spaced apart limit positions by the powerunit 18 in order to convert a torque applied to the carrier intosubstantially radial forces acting on the punching units 20, 22, 24 and26 to efect radial movement of punching tools respectively connectedthereto in a manner more fully described below.

It is to be understood that the number and arrangement of punching unitsand cam assemblies disclosed herein is for illustrative purposes only,since it is within the scope of the invention to place as many punchingunits as may be desired 'around the tooling, and to peripherally spacethem in any desired manner whether equidistant or otherwise. It is alsowithin the scope of the invention to offset the path of movement of, andthe direction of force applied to, the punching units so that thearticle is punched with a hole the axis of which is on a chord of thearticle rather than on the diameter thereof, assuming the article isother than rectangular in cross section.

It should further be understood that the machine of this invention maybe used with only a single punching unit to punch either one aperture ina blank or a single row of apertures extending axially of the blank.

Referring now to FIG. 4 for a more detailed description of the presentmachine, the tooling 16 comprises essentially a central elongate hollowmandrel or die post 38 which will have an exterior configurationconforming generally to the interior configuration of the part to bepunched. The die post 38 has a plurality of apertures 40 extendingradially through the wall thereof for cooperation with a plurality ofpunching tools described below, and is further provided with a bottomoutwardly projecting annular ange 42 by means of which the die post 38is removably secured, as by the screws 44, to the upper surface of a dieset ring 46 which in turn is connected, as by the screws 48, to theframe 10. The location and arrangement of the apertures 40 in the diepost will depend upon the nature of the punching pattern desired on thefinished article.

The tooling lfurther comprises a punch block 50,

which may either be annular as shown in the drawings, or it may besegmental. The punch block 50 is provided with a plurality ofperipherally spaced rows of vertically spaced apart bores 52, each borebeing provided with a bushing 54 in 'which a working tool 56 is adaptedto slide. The punch block is removably secured to the die set ring 46 bymeans of bolts 58 which extend axially through the punch block, thelatter also being provided with a counter-bore 60 which overlies theannular flange 42 of the die post 38.

It will now be understood that the above described structure, with theexception of the die set ring 46, is not a permanent part of themachine, but rather is removable and is custom designed for each type ofworking operation to be performed on a particular article.

The punching units 20, 22, 24 and 26 are substantially identical, andcomprise a ram g-uide 62 which is secured to the die set ring 46adjacent the outer edge of the latter. Each ram guide 62 is providedwith opposed laterally extending wings 64 (FIG. 1) which overlie aT-slot 66 formed in the die set ring 46. A headed bolt 68 passes througheach wing 64 and is threadedly engaged with a nut 70 disposed in theT-slot 66 so that by tightening up on the nut 70 by the bolt 68, the ramg-uide 62 is secured to the die set ring. It Iwill be observed that theram guide may be securely locked in any desired angular position on thedie set ring merely by loosening the bolts 68 for the particular ramguide, moving it angularly to the desired position and retightening thebolts. It will be noted that the headed bolts 48 which secure the dieset ring 46 to the frame 10 -are recessed into suitable counterbores inthe bottom of the T-slot 66 so that the nuts 70 secured to the bolts 68may pass over the tops of the bolts 48 while adjusting the position ofthe ram guide 62 to suite a desired punching pattern.

Each ram guide is further provided with a pair of radially extendingbores 72, each bore being provided with a bushing 74 for receiving andguiding a pair of rams 76 for reciprocable movement in the ram guide 62.The rams are connected at their inner end to a tool carrier or ram head78 by means of a pin connection 80 so that the rams support the toolcarrier 78 for movement therewith. Thus as the rams are reciprocated bymeans hereinafter described, the ram head and the tools 56 carriedthereby are reciprocated radially of `the punch block 50 to perform theworking operation.

Each ram head 78 comprises an elongate rectangular block 82 to which therams 76 are connected, and another block 84 which has an open endedT-slot 86, or other suitable configuration, extending the length of theblock 84, the block 82 being secured to the block 84 by means of thescrews 88 as seen in FIG. 1. lEach of the tools 56 is provided with aT-head 90 which is shaped to substantially lit within the T-slot 86y ofthe block 84, so that the tools are thus engaged with the ram head 78 indriving relationship in both directions of movement. The reason for thesplit ram head 78 is that, by loosening the screws 88 and insertingextremely thin shims at the interface between the blocks 82 and 84 andretightening the screws 88, the working end of the tools 56 can bemaintained in precise relationship with the work even though some wearand tear may have slightly shortened the tools. This is quite criticalin operations which do not require that a hole be punched through thetubular blank, such as with shaped depressions or detents, serrating orlancing to provide spring fingers, etc., in which the extent ofindentation of a detent linger is critical.

Another advantage obtained by the construction of the ram headconnection between the rams 76 and the tools 56 is that there is sucientplay in the T-slot connection between the ram head and the tools toassure that only absolutely axial forces are transmitted from the ramsto the tools even though some non-axial driving forces are applied bythe ram actuating means to be presently described to the rams. By thusassuring the axial alignment of the driving forces applied to the tools,Wear and tear on the tools and the tool bushings 54 is held to a minimumso that the machine maintains an extremely high degree of punchingaccuracy over a long period of time.

yIt will also be appreciated at this point that, because of the T-slot86 and T-head 90 type of connection between the ram head 78 and thetools 56, by merely removing the screws 58 it is possible to remove theentire punch block 50 and all the tools carried thereby without anyother disassembly of the machine. This is advantageous where, forexample, it may be desired to run a subsequent batch of blanks withdifferent tools where it is not necessary to rearrange the loc-ation ofthe punching units as a whole.

The rams 76 are reciprocated :by the actuating cam assemblies 28, 30, 32and 34 which, in the preferred form of the invention, comprise aplurality of elongate block like cam members 92, 94, 96 and 98. Each camis secured to the carrier ring 36 for movement therewith by means ofbolts 100 which pass through the cams and are threadedly engaged withnuts 102 which are disposed in a circular T-slot 104 formed in aninturned flange 106 which is an integral part of the carrier ring 36.The T-slot 104 in the carrier flange 106 provides the same advantage ofinfinite position adjustment of the cams on the carrier as does theT-slot 66 in the die set ring 46 with regard to simliar adjustment ofthe angular position of the ram guides 62. It will be apparent that whensetting up the actuating components 14 of the machine in conjunctionwith the tooling 16 for performing a particular working operation, thecams and the ram guides would be adjusted in the desired positionsimultaneously and all of the necessary bolts then tightened to securethe actuating parts in the desired position.

Each of the cams, as best seen in FIG. 4, is provided with a pair ofelongated slots 108, in the bottom of which is secured a hardened wearplate 110 as by the screws 112. The radial inner face of each cam hassecured thereto a plurality of similar wear plates 114, 116 and 118, allas by the screws 120. It will also be observed in FIG. 4 that the plates114, 116 and 118 are made wide enough so as to overlap the openingleading into the slots 108 so that the radial outer surfaces of theseplates dene a bearing surface against which the cam followers mounted onthe outer end of the rams 76 ride, the plates 114, 116 and 118effectively capturing the cam followers within the slots 108. By thisconstruction, the cams are effective so forcibly dri-ve the rams 76 inboth directions of movement, thereby providing a position means ofwithdrawal of the punches from the work after the working operation hasbeen completed.

The cam followers comprise a pair of wheels 122 which are secured to thereduced outer end portion 124 of each ram by means of an axel 126suitably pinned to each ram so that as the cams oscillate back andforth, there is a smooth, frictionless engagement between the cams andcam followers. This construction further assures maintaining a highdegree of accuracy of the machine over a long period of time.

As already indicated, the cams are oscillated by means of the carrier36, the latter having an opstanding flange portion 128 which providesadditional support for the cams to relieve the high shearing forcesimposed on the screws 100 by the resistance to deformation of thearticle being punched. The carrier has a shaped inner annular edge 130on the flange portion 106 which cooperates with a correspondingly shapedouter edge portion 132 formed on the die set ring 46, which therebyguides the carrier :for arcuate movement in a fixed circle. A pluralityof hardened wear plates 136 are secured to the frame 10` as by thescrews 138 on which the carrier rides.

As best seen in FIGS. 1 and 3, the carrier 36 is provided with a lug 140to which a piston shaft 142 is pivotally connected by means of a clevis144 and a pin 146. The

piston shaft 142 is xedly connected to a piston head 148 whichreciprocates in a cylinder 150, the latter being pivotally connected tothe frame 10 by means of a bushing 152 in which a pin 154 connected tothe cylinder rotates, and another bushing 156 within which another pin158 connected to the cylinder rotates, the bushing 156 being fastened tothe upper cross bar 160 of a U-shaped bracket 162 secured to the frame10. From the foregoing it is seen that reciprocation of the piston head148 within the cylinder 150, by means hereinafter described, impartsoscillatory movement to the carrier 36 and corresponding oscillatorymovement to the cams 92- 98 over a predetermined arc which iscoordinated with the length of the cams.

The punching machine operates, in accordance with the principles of thepresent invention, in the manner now to be described. The carrier 36 andthe actuating cams are driven by the piston rod 142 in a unidirectionalmovement to effect one complete cycle of operation of the punching tools56 from a withdrawn position to a punching position and back to thewithdrawn position. Thus movement of actuating parts is maintained at aminimum during the working cycle which not only reduces wear and tear onthe moving parts but also substantially increases the productionefficiency of the machine.

The radially spaced camming surfaces defined by the wear plates and 114,116 and 118, as seen in FIGS. 1, 5 and 6, are formed to be rectilinearand are disposed in alignment with chords of a circle dened by thearcuate movement of the ends of the camming surfaces in theiroscillation over a predetermined arc. They are also of sufficient lengththat they are in continuous engagement with the wheels 122 throughoutthe extent of movement of the cams. Therefore, the camming surfaces aredisposed gradually closer to the longitudinal axis of the die post 38from either outer end of the camming surfaces toward the midpointsthereof. Thus, as the carrier rotates from one end position as shown inFIG. 5 toward the intermediate position shown in FIG. 1, the camfollower wheels 122 and all of the actuating parts connected thereto aremoved radially inwardly to effect a punching operation.

The cams are disposed on the carrier in such position that the camsurfaces are perpendicular to the axes of the rams when the cam surfacesare bisected by the axes of the rams, and this occurs when the rams arein their radially innermost position. 'Ihus the arrangement is such thatthe force transmitted from the cams to the cam followers is increased asthe rams and punches approach punching position, since the force actingon the rams is gradually shifted from a radially acting component of anonradial force to a completely radial force acting on the rams. Thisforce reaches a maximum when the cam surfaces are perpendicular to theaxes of the rams. This construction has the advantage of applying thegreatest speed of movement of the rams as the tools approach a punchingposition, and gradually diminishing the speed of the rams but increasingthe working force applied thereto as the midpoint of the cam surfacesapproaches the cam follower wheels, that is, when the straight line camsurface is substantially perpendicular to the axes of the rams.

It will now be understood that the extent of radial movement of the ramsand working tools is determined by the difference in radial distancefrom the axis of the die post 38 to the midpoints of the cam surfacesand the ends thereof respectively.

As the carrier 36 continues to rotate in the same direction and movesthe cams from the punching position of FIG. 1 toward the other endposition shown in FIG. 6, the rams 76 are moved radially outwardly towithdraw the working tools by the action of the cam surfaces defined bythe wear plates 114, 116 and 118. The rams and working tools are fullywithdrawn when the cams are moved sufficiently far to dispose the otherends thereof in engagement with the rollers 122. It is now apparent thatthe rams are formed to have a length sufficient to be in continuous andbidirectional driving relationship with the cam followers throughout theextent of movement of the carrier 36 in one direction between its limitpositions so that the rams and working tools are moved both radiallyinwardly and outwardly to punch and withdraw in response to a single,uninterrupted unidirectional movement of the carrie 36. A reversemovement of the carrier 36 from the position shown in FIG. 6 to that ofFIG. will effect another complete punching operation.

At the end of each punching operation, i.e., when the cams are moved bythe carrier to the FIG. 5 or FIG. 6 position of the parts, the ejectormechanism mounted on the underside of the frame 10 is actuated by meansto be hereinafter described to eject the part from the die post 38 in anupward direction. As best seen in FIG. 4, the ejecting mechanismcomprises a supporting plate 170 mounted under the frame 10 by means ofbolts 172 which are threadedly engaged with the frame 10 and to whichthe plate 170 is secured by screws 174. The bolts 172 form guide rodsfor guiding a ram plate 176 for vertical reciprocatory movement, the ramplate removably carrying a plurality of spaced ejector pins 178 havingheads 180 captured between a plate 182 which is screwed to the ram plate176. The ejector pins pass through elongate slots 184 so that theejector pins 178 underlie the bottom of the part being punched, therebyeliminating any tendency for the pins to slip over the outer wall of athin part and fail to eject it.

The ram plate 176 is driven by a piston rod 186 which passes through ahole 187 formed in the plate 170 and is threadedly engaged with the ramplate, the piston rod being connected at its other end to a piston 188reciprocably mounted within an air cylinder 190. The cylinder 190 isconnected to the support plate 170 by screws 192. The part is ejectedfrom the die post 38 by operation of the piston 188 to raise the ejectorpins 178, the piston being operated in both directions in timedrelationship with operation of the carrier 36 when the latter reaches aterminal position by control means hereinafter described.

A more thorough understanding of the control components of the machineand its mode of operation will be obtained by reference to FIG. 7,wherein the carrier actuating piston 148 and cylinder 150, and theejector mechanism piston 188 and cylinder 190 are all shownschematically, together with other control components. The piston 148 isreciprocated by air from lines 192 and 194 by alternately delivering airto one side of the cylinder 150 through one line and simultaneouslyventing the other side of the cylinder through the other line. Thepiston 188 for the ejector mechanism is reciprocated in the cylinder 190in the same manner by means of air lines 196 and 198.

The flow of air in lines 192 and 194 is controlled preferably by afour-way spool valve 200 having a cylinder 202 in which a spool 204 isreciprocated by solenoids 206 and 208, the spool selectively controllingthe flow of air in the lines 192 and 194.

The flow of air in lines 196 and 198 is controlled by another spoolvalve 210 which is substantially identical to the valve 200, having acylinder 212, a spool 214, and solenoids 216 and 218 for reciprocatingthe spool.

An impulse type start switch 220 of known construction is provided foractuating the solenoids 206 and 208 alternately. A pair of normally openimpulse type limit switches 222 and 224 are provided at the limitpositions of the stroke of the carrier 36 (see FIG. 6) and are actuatedby any suitable actuator 226 carried by the clevis 144 on the outer endof the piston rod 142, the switches 222 and 224 serving to control thesolenoid 216 on the ejector spool valve 210. The other solenoid 218 onthe ejector spool valve is controlled by a similar impulse type limitswitch 228 which is secured to the underside of the frame 10 (see FIG.4) in position to be contacted by an 3 actuator 230 suitably carried bythe ram plate 176 when the latter reaches the end of its ejectingstroke.

The remaining elements of the control mechanism described above will beexplained in connection with a description of a complete cycle ofopeartion of the machine, which is as follows: Commencing with thecarrier 36 and the associated parts in the position illustrated in FIG.5, depression of the start switch 220, either by a ringer or footoperated pushbutton 232, momentarily moves the switch blade 234 to theleft as viewed in FIG. 7, thereby completing a circuit from the mainlead 236 through a lead 238, a lead 240, the switch blade 234, a lead242, through the winding of the solenoid 206 and a lead 244 back to theother supply lead 246. Energization of the solenoid 206 forces the spool204 toward the right, whereupon air enters through the inlet port 248and thence through the line 194 into the left side of the cylinder todrive the piston 148 toward the right. Simultaneously, air in the rightside of the cylinder 150 is vented through the line 192 and the exhaustport 250 of the control valve 200. This action rotates the carrier 36 ina counterclockwise direction from the position shown in FIG. 5 to thatshown in FIG. 6 thereby causing a complete punching and withdrawaloperation of the working parts of the punching units as described above.

When the carrier 36 reaches the end of its stroke7 the actuator 226closes the impulse switch 224 to effect a momentary closing of a circuitfrom the supply lead 236 through a lead 252, the switch 224, a lead 254,the winding of the solenoid 216, and a lead 256 to the other supply lead246. Energization of the solenoid 216 causes the spool 214 to be movedtoward the right, whereupon air enters through the inlet port 258 andflows through the line 198 to the left side of the cylinder 190.Simultaneously, air inl the right side of the cylinder is vented throughthe line 196 and the exhaust port 260 of the valve 210. This actioncauses the piston 183 to be driven toward the right, whereby the ejectorpins 178 connected to the piston forcibly eject the part from the diepost 38.

When the ejector piston 188 reaches the end of its stroke, the actuator230 carried by the ejector ram plate 176 closes the impulse switch 228which causes a momentary closing of a circuit from the supply lead 236,the winding of the solenoid 218, a lead 262, the switch 228, and a lead264 back to the other supply lead 246, which energizes the solenoid 218to cause the spool 214 to move toward the left. This movement permitsair to enter through the inlet port 258 and through the line 196 to theright side of the cylinder 190, whereupon the piston 188 is returned tothe position shown in FIG. 7, the air on the left side of the cylinder190 now being vented through the line 198 and the exhaust port 266. Thusthe ejector mechanism is instantly returned to its normal position andanother part may be placed on the die post 38 preparatory for the nextcycle of operation.

When the start switch 220 is again actuated after the next blank isplaced on the die post 38, the switch blade 270 momentarily moves towardthe right to complete a circuit from the supply lead 236 through thelead 238, the switch blade 270, a lead 272, through the winding of thesolenoid 208, and a lead 274 back to the other supply lead 246.Energization of the solenoid 208 moves the spool 204 toward the leftback to the position shown in FIG. 7, whereupon air enters through theinlet port 248 and ows hrough line 192 to the right side of the cylinder150, whereupon the piston 148 is moved toward the left, the air in theleft side of the cylinder 150 being vented through line 194 and theexhaust port 276 of the valve 200. Movement of the piston 148 toward theleft drives the carrier 36 in a clockwise direction to perform anotherpunching and withdrawal operation as above described.

When the carrier reaches its clockwise terminal position, the actuator226 closes the momentary switch 222 which completes a circuit from thesupply lead 236 9. through the lead 252, a lead 278, the switch 222, alead 280, the lead 254, the so1enoid'216 and the lead 256 back to theother supply lead 246, whereupon energization of the solenoid 216initiates a complete cycle of operation of the ejector mechanism asdescribed above.

It is apparent from the foregoing that there is provided a multiple sidepunching machine `Vwhich achieves the foregoing objetcs and avoids thedisadvantages of prior art machines. It is to be understood that theinvention is not to be considered as limited vto the specific construction and mode of operation described hereinabove and shown in theaccompanyingdrawings, which is merely illustrative of the principles ofthe invention and which is susceptible to variation of form, size,detail and arrangement of parts, the invention being intended to coverall such variations and modifications thereof as may be deemed to bewithin the scope of the appended claims.

What I claim is:

1. A machine for multiple side punching of tubular blanks comprising:

(A) a frame,

(B) means on said frame for supporting a tubular blank,

(C) a plurality of angularly spaced punching units disposed around saidsupporting means, each punching unit comprising (l) a ram guide havingmeans for supporting and guiding a ram for reciprocable movementradially with respect to said blank supporting means,

(2) a ram disposed in said guiding means, and

(3) means carried by the radial inner end of said ram for connecting aWorking tool thereto,

(D) an annular carrier rotatably supported on said frame,

(E) means for oscillating said carrier through a predetermined angle ofrotation between spaced apart limit positions,

(F) cam means mounted on said carrier in driving engagement with theradial outer end of said rams, said cam means including means formed tobe in continuous and bidirectional driving relationship with said ramsthroughout the extent of movement of said carrier in one direction so asto drivingly interconnect said carrier and said plurality of rams tosimultaneously forcibly drive said rams both inwardly and outwardly inresponse to a single unidirectional movement of said carrier betweensaid limit positions,

(G) ejecting means mounted on said frame adjacent said blank supportingmeans for ejecting a blank therefrom, and

(H) means responsive to the arrival of said carrier in both said limitpositions for actuating said ejecting means upon completion of eachsingle unidirectional movement of said carrier.

2. A machine as set forth in claim 1 wherein said cam means comprises aroller carried by the radial outer end of each ram, and correspondingplurality of substantially elongate blocklike cam members each having anelongate slot formed therein with an elongate hardened wear platedisposed in the bottom of said slot and a plurality of correspondinglyelongate hardened wear plates disposed at, and partially blocking, theentrance to said slot and effectively capturing said roller within saidslot, said wear plates defining a pair of radially spaced inner andouter cam surfaces to drive in response to the forces on said rollers bysaid wear plates said rams both inwardly and outwardly.

3. A machine as set forth in claim 2 wherein said cam members aredisposed on said carrier in position to have said cam surfacessubstantially perpendicular to the axes of said rams when the latter arealigned with the midpoints of said cam surfaces whereby the cammingforce approaches a maximum as the rams reach their radially innermostworking position.

4. A machine for multiple side punching of tubular blanks comprising:

(A) a frame,

(B) means on said frame for supporting a tubular blank, (C) a pluralityof angularly spaced punching units disposed around said supportingmeans, each punching unit comprising (l) a ram guide having means forsupporting and guiding a ram for reciprocable movement radially withrespect to said blank supporting means,

(2) a ram disposed in said guiding means,

(3) means carried by the radial inner end of said ram for connecting aworking tool thereto,

(D) an annular carrier rotatably supported on said frame,

(E) means for oscillating said carrier through a predetermined angle ofrotation between spaced apart limit positions, V

(F) cam means interconnecting said carrier and said plurality of. ramsfor simultaneously forcibly driving said rams both inwardly andoutwardly in response to a single unidirectional movement of saidcarrier between said limit positions, and

(G) means for adjustably securing said ram guides to said frame and saidcam means to said carrier at any peripherally spaced location aroundsaid blank supporting means, said means including a pair of concentricsubstantially T-shaped recesses formed in said frame and said carrierrespectively, and means on said ram guides and said cam meanscooperating with said recesses and slidable therein to a desired angularlocation for securing both the rams guides and cam means in said desiredlocations.

5. A machine for multiple side punching of tubular blanks comprising:

(A) a frame,

(B) means on said frame for supporting a tubular blank,

(C) a plurality of angularly spaced punching units disposed around saidsupporting means, each punching unit comprising (l) a ram guide havingmeans for supporting and guiding a ram for reciprocable movementradially with respect to said blank supporting means,

(2) a ram disposed in said guiding means,

(3) a punch block secured to said frame and having means for supportingand guiding a punching tool for reciprocable movement radially withrespectl to said supporting means, and

(4) a punching tool slidably received in said punch block supportingmeans,

(D) an annular carrier rotatably supported on said frame,

(E) means for oscillating said carrier through a predeterminedtangle ofrotation between spaced apart limit positions,

(F) cam means interconnecting said carrier and said plurality of ramsfor simultaneously forcibly driving said rams both inwardly andoutwardly in response to a single unidirectional movement of saidcarrier between said limit positions, and

(G) means carried by the radial inner end of each ram between said punchblock and said ram guide for connecting said punching tools to saidrams, said connecting means including means for transmitting only an'axial driving force from said rams to said punching tools while anonaxial driving force is peing imparted to said rams by said cam meansso that such nonaxial driving force is not transmitted to said punchingtools.

6. A machine as set forth in claim 5 wherein said punch block includesmeans for removably securing said punch block to said frame, and saidconnecting means includes means for removably connecting said punchingtools to 11 said rams by movement of said punching tools axially of saidblank supporting means whereby said punch block, together `with saidpunching tools therein, can be withdrawn from the machine by movementaxiallyv of said blank supporting means and thus disconnected from. saidrams.

7. A machine as set forth in claim 6 wherein said means for removablyconnecting said punching tools to said rams comprises a ram head carriedby the radial inner end of each ram, an elongate hollow substantiallyT-shaped recess formed in said ram head and opening radially inwardly,said punching tool having an enlarged substantially T-shaped head formedon its radial outer end which substantially corresponds to the shape ofsaid recess whereby said tool head may be inserted into said recess andremoved therefrom through the open end of the recess.

8. A machine as set forth in claim 5 wherein each of said connectingmeans comprises a ram head formed of two separable lbody members, one ofsaid body members being carried by said ram, the other of said bodymembers having means for securing said working tool thereto,

References Cited UNITED STATES PATENTS 2,374,301 4/1945 Olney 83-1942,419,534 4/ 1947 Burleson 83-194 2,513,710 7/ 1950 Brauchler 7241022,514,507 7/1950 Mueller 72-402 3,316,787 5/1967 Lambro 83-109 CHARLESW. LANHAM, Primary Examiner E. M, CoMBs, Assistant Examiner U.S. Cl.X.R.

